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July 28, 1942. i-a. T. Avg-:m

CALCULATING MACHINE Original Filed Jan. 23, 1935 8 SheeisSheec l INVENTOR HAQQLD TAI/.59V

ATTORNEY July 28, 1942- H. T. AVERY CALCULATING MACHINE Original Filed Jan. 23, 1933 8 Sheets-Sheet 2 INVENTOR HAQOLD TA VEPY ATTORNEY July 2s, 1942. ,.1 AVERY 2,291,136

CALCULATING MACHINE Original Filed Jan. 23, 1933 8 Sheets-Sheet 3 I'LIE'- E- INVENTOR HAPULD 7341/5/21/ ATTORN EY July 28, 1942- H. T. AVERY CAL'CULATING MACHINE Original Filed Jan. 23, 1935 8 Sheets-Sheet 4 7U E 1 F INVENTOR HAPOLD. TAVEQY ATTORN EY July 28, 1942. H. T. AVERY CALCULATING MACHINE 8 Sheets-sheet s Original Filed Jan. 25, 1933 |m lm HJmu INVENTOR HAPoLD TAL/EDY ATTORNEY July 28, 1942.

H. T. AVERY CALCULATING MACHINE Original Filed Jan. 23, 1933 8 Sheets-Sheet 6 im immwrmw UHI mmm mmm INVENTOR HAPOLD TAW/2y ATTORNEY Jul'y 28, 1942.- H. T. AVERY CALCULATING MACHINE Original Filed Jan. 23, 1933 8. Sheets-Sheet 7 PIE 113- @XM/W R my N E E M mf 4 A T. um, J D MUM: m MW A w H 5 n ./Z 4 y n H M m/TMMJQ, [4 ,r Cry W H HUH. u L nu u HU u W HMH u u Hu nu 1 1N y# w J m ha f .mf

ATTORNEY July 28, 1942. H. T. AVERY 2,291,136

l CALGULATING MACHINE P1515.. v F1515- INVENTOR HAPULD TAV/SPY ATTORNEY Patented `lilly 28, 1942 ZZQMB@ FCE CDALCTUATHNG MACHKNE Harold 'li. Avery, ibalrland, Calif., assigner to Marchant Calculating Machine Company, a corporation of California Original application Jianuary 23, i933, Seriai No.

Divided and this application Decemloer 3, 1940, Serial No, 368,299

(Cl. 23S- 62) ii cams...

The present invention relates to calculating machines capable of automatically performing division calculations, such a machine being disclosed in the copending application of Harold T. Avery, Serial Number 653,207, iileclA January twenty-third, 1933, of which the present application isa division. Said application has since matured into Patent Number 2,229,630 issued on January 28, 1941. Reference may be had to the above patent for a description of a complete calculating machine including mechanism' not specifically disclosed herein. it is to be understood, however, that although vthe invention is shown as applied to a machine of the4 general type disclosed in the above patent the invention is l also applicable to other types.

it is the general object of the present invention to provide an improved division control mechanisml for a calculating machine. l

Another objectfof the invention is to provide a register controlled automatic division mechamsm which will not impede the operation. of the register mechanism.

In certain types of accumulator register mechanisms, such as those provided with geared tens carrying mechanism, one example of which is disclosed in the above mentioned Avery patent wherein the entry of amounts, or digitation and the tens carrying are simultaneously eiected, spring operated parts are employed for causing sequential movements of a series of dials from to 9 in registering an overdraft. Due to this feature of construction of such mechanisms, any impedance of the dials or mechanism connected thereto,A caused by the association therewith of overdraft sensing mechanism, may interfere with operation of the dials especially in registering overdrafts. The present invention avoids such impedance of the register by an overdraft sensing mechanism by providing sensing mechanism arranged to be spring operated and merely released by the accumulator register instead of actually operated thereby, upon the cccurrence of Ian overdraft. This is accomplished by providing register actuated snail cams cooperating with cam follower means; the cams being so arranged that upon the occurrence of an matic division mechanism in machines in which calculating machines of` lil the registering mechanism may remain in constant engagement with its actuating mechanism throughout a series of cycles of operation of the latter.

A further object of the invention is to make possible,l selectively, either continuous driving at 4a uniform speed oi the actuating mechanism o riage taken at different points.

Figure 5 is an enlarged view, partly in section, illustrating two of the accumulator register dial assemblies.

Figure 6 is a detail View in elevation, illustrating the means for raising and lowering the dipping portion of the carriage.

Figure 6A is afdctail side View illustrating the cam operated means for releasing the latches i to enable dipping of the dipping portion of the carriage.I

Figure 7 is a ,detail side view illustrating mechanism for releasing the dipping portion of the .carriage from its dipped position.

Figure 8 is a side elevational view illustrating the control of the setti-ng clutch, main clutch, and motor switch.

Figure 9 is a side elevational view illustrating part of the division control mechanism including the division key and the sensing mechanism.

Figure 10 is a fragmentary plan View of part of the overdraft sensing mechanism.

Figure 11 is a fragmentary side view illustrating the'construction of levers carried by the pulsating shaft 633.

Figure 12 is a detail view, partly in section, illustrating the main clutch, the reversible division drive mechanism, and the main reverse unit.

Figure 13 is a sectional view taken substantiallyA along the line l3-i3 of Figure 12.

Figure 14 is a schematic view illustrating in' Figures 18 and 19 are end and side views, respectively, of one of the levers controlled by the division key during a division operation.

Figure 20 is a side view illustrating the overdraft sensing mechanism in different positions.

The machine in connection with which the present invention is disclosed is of the proportional gear type wherein each accumulator register dial is cyclically driven at a speed proportional to the value selected to be entered therein.

Manually set selection mechanism The machine is of the key set type in which means are provided for setting factors of a calculation upon a keyboard and subsequently operating the machine under power.

As viewed in Figure 1, each bank of value selecting keys comprises a channel-shaped key frame |0| in which the key stems |03 of the various keys |00 are slidably mounted. Compression springs |02 normally maintain all of the keys |00 in raised positions.

All of the key stems |03 are of the same length and each has a cam extrusion |06 which, upon depression of the associated key, pushes to the right a slotted key locking slide |04 slidably supported on the lower side of the channel |0|, thereby releasing any other latched down key. in the same key section. Upon full depression of any value key the slide 0| is returned to its initial 1ocation by spring |05 and, by overlapping the upper end of the extrusion |06, latches the depressed key.

Disposed underneath the value keys |00 in each key bank is adierentially settable bar which is suspended from the key frame |0| by means of two parallel links 2| and |22. This bar |20 has nine identical divergent notches |23, each of which terminates in a rectangular slot |24 proportioned to receive the end of a respective key stem |03 so that the bar |20 will be accurately positioned thereby. The key stems |03 are spaced equal distances apart, each such distance being slightly greater than the spacing between successive slots I 24, so that each succeeding slot |24 will be spaced one increment further away from its cooperating key stern, Thus, depression of a value key will cam the bar |20 to the right, as viewed in Figure l, a number of increments equal to the value represented by the depressed key.

Such movement of each of the bars |20 is utilized to set up a mechanical representation of the selected value to control the calculating mechanism accordingly, and for this purpose a segmental rack gear |26 is formed integrally with each of the rear suspension links |22. This rack |26 engages a pinion |25 fixed to a gear |28 mounted on a cross rod |21. Gear |28 is entrained with a gear through an idler |40, which is normally held in the position illustrated in Figure `1 by a tension spring |42 tending to maintain the selection mechanism at zero selection.

Gear |20 also meshes with a pinion |3| mounted on a cross rod |32 and secured to a check dial |36 which is visible through an opening |33 in a cover |34 to indicate the value of a factor set up in the keyboard.

Attached to each gear |45 is a cam unit generally indicated at |46, which is positioned by rotation of the gear |45 to form a mechanical representation of a value set up on the associated key bank.

Each cam unit |46 comprises tive cams integrally secured together, one oi' such cams being illustrated in Figure l. points |40 and two low points |40 on its periphery and such cams are so staggered that no high point or low point on one cam is aligned with a high or low point on another cam. Also, it will be noted that the respective high and low points of each cam are diametrically opposite each other,

As is described in detail in the above mentioned Avery patent, the various cams on the cam unit |46 in each order of the machine are so arranged that upon depression of a value key |00, the gear |46 will be rotated to position the cam unit |46 so that one ofthe high points of one of the cams will be positioned in the path oi' a nose |83 of one of a set of five feeler arms |8| on one side of the cam unit |46, or in the path of a nose |00 of one of a set of five feeler arms |81 at the other side of the unit |46.

Power set selection mechanism After the setting of the mechanism heretofore described has been completed and upon manipulation of one of the operation control keys such as the division key (Figure 0), the power operated portion of the machine is brought into operation and acts under the control of the various cam units |46 to effect entry of a value set up on the keyboard into the accumulator register. Since this power operated mechanism is disclosed in detail in the above mentioned Avery patent only a brief' description of the function of this mechanism is deemed necessary herein.

Upon depression of an operation control key, such as an add key (not shown) or the division key 100, a setting clutch dog 356 (Figure 8) is rocked, as will be described in more complete detail hereinafter, to effect engagement of a cycli cally operable setting clutch 361, the details of which are also disclosed in the above Avery application.

Upon engagement of the setting clutch 361, power derived from a motor (not shown) is transmtted through the clutch to a setting shaft 36|. A number of pairs of complementary cams identical to cams |00, |0| (Figure l) are keyed to the setting shaft35l, and each such pair has an associated cam follower |04 pivoted on a cross shaft |06 and provided with a roller |02 in engagement with the cam |00 and a second roller |03 in engagement with the cam |0I. As the shaft 35| rotates the cam followers |04 are rocked first, in a clockwise direction and, through links |06, impart a counter-'clockwise rocking movement to a series of levers |84a pivotally mounted on a shaft |05.

A shaft |04 supported by the levers |04a has pivotally mounted thereon the group of feeler arms |0| hereinbefore mentioned, one of these groups being located adjacent each of the cam units |46. During the leftward movement of the feeler arms |8| (as viewed in Figure 1) by the shaft 04, each of the noses |03 formed on the feeler arms |0| engages the periphery of its associated cam on the cam unit |46, thereby causing Each cam has two high 1 agentes each feeler arm |8| to pivot about the point of contactbetween its nose and the periphery of its associated cam. The balance of the forward movement of the shaft |84 by the cam followers |94 elects leftward movement of the lower ends of each of the feeler arms |8| and this movement is transmitted through a link |86 to a second feeler arm |81 aligned with each of the feeler arms |8|. The arms |81 rock in a clockwise direction about a fixed shaft |88 until their noses |89 engage the periphery of the respective'cams at points diametrically opposite lto Athose engaged bythe noses |83 of the associated feeler arms |8 Thus, one of the feeler` arms |8| will be rocked a considerable angle'about its usupporting' shaft |84 to oneside or the other of a medial position, depending upon Whether its nose |83 is in engagey ment with a high point |46 or a lowpoint |59 of its respective cam'. yAll of the noses |53 of the other feeler arms |8| and the noses |59 of their respective aligned arms |81 will be heldthe same distance apart from the cam supporting shaft |41, since they will engage the illustrated conchine. Arranged on each plate |55 is a gear |55 entrained with a laminated gear unit |55 cornpriising several gears keyed on the respective sleeve |53 intermediate adjacent plates |55.

From the above it will be seen that four of each group of ve of the selection plates |55 will be held in a medial position as shown in Figure 1, while the iifth will be moved forward or rearward until the gear |51 thereonmeshes with an aligned gear as at |62 on a quarter speed shaft Accumulator mechanism From the foregoing description of the selection mechanism it is apparent that a number comprising a plurality of digits can be registered upon the several gear units |66 by differentially driving the gears various distances proportionate to the quantitative relation of the several digits comprising the number. ln orderl to visually indicate the number of increments of movement of the gear units |66, as well as to advance a superior registering elementI one extra increment whenever the next lower element lhas made a complete rotation, an accumulator mechanism is provided, being mounted 4on a. transversely shiftable carriage 200 (Figures 1, 3, and 4).

The carriage is supported in the machine for transverse shifting in either direction by rollers and 284 on opposite sides of the carriage.

' The carriage includes a track strip 201 connected lformed at the upper end of the bracket 253 to retain the front of the carriage in place. At the rear of the carriage, the rollers 200 are rotatably mounted on a bracket 285 extending from the machine frame, which rollers engage a track strip 255 carried by the carriage. The strip 285 is guided between the rollers 285 and hooks formed at the upper end of the bracket 285 to support and retain the rear of the carriage in place.

' bail, by means of which. the entire body of |5| or an aligned gear as at 6| on a half speed shaft |50.

Gears |6| and |62 are two of a set of nine gears located on the shafts and |5| and positioned in each order of the machine. The shafts |50l and l5| are connected to the'drive motor (not shown) through a cyclically operable main clutch 480 (Figure 14) in such a manner that` 'the shaft |50 is rotated through '180 for each cycle of operation of the clutch and shaft |5| is rotated through 90@ for each cycle of operation of the clutch. The diameters of the various gears on the shafts |50 and |5|, such as the gears |6| and |62, are so arranged that for each machine cycle the gear unit |66 will be rotated by one of the gears on the shafts |50 and |5| a partial revolution comprising a number of increments corresponding to the value of a key |00 which is depressed during a selection operation. If no key is depressed the selection plates will' be soarranged that none of the gears on shafts |50 and |5| will become operative to drive the gear unit f of three notches |99 in each selection plate |55. This locking gate |91 is operated by means of a .suitable cam carried by the setting shaft 35| as described in the' above Avery patent.

plates 2 |4 may be oscillated about shaft 2 I3 during operations hereinafter described, in which description of the'mechanism supported by the plates 2|4 will be referred to as the dipping portion of the carriage.

The various denominationally arranged units .of the accumulator are assembled on a rod 2|6 supported by the plates 2M, there being one of such units between two adjacent plates 2|4, and each unit is adapted to be driven by one of the aforementioned gear` units |66 (Figure` 1) with which intermediate gears 2|5, rotatably mounted on shaft 245 (Figure 4) and entrained with the gears 228 of the several accumulator units, may bemeshed by lowering the dipping portion of the carriage as will be described hereinafter.`

Referring more particularly to Figure 5, it will be noted that each accumulator unit or order i' comprises a spider 2 which is rigidly secured to a sleeve 2|8 on the `rod 2|6. The spider 2|1 carries an internal ring gear 2|9 on its right hand side which is spot welded or riveted to the flared out portion 220 of the spider. A thin dial shell 222 is xed to the internal gear 2|9 and spider 2 I1 and has formed around the periphery thereof a number of progressively arranged digits from 0 to 9. Integral with thesleeve 2|8 surrounding the rod 2|6 is a sun gear 223 abutting a Iplate 2|4, and interposed between the sun gear 223 and the spider 2|1 is a snail cam 224 and spacer 225. The snail cam 224 has a small aperture therein into which extends a lateral projection 226 of spider 2| 1, thus causing the cani and spider to rotate as a unit with the internal gear 2I9 and the sun gear 223.

Immediately to the right of the mechanism just described is a large knurled disc 221 iixed to a spur gear 228. These elements are rotatably mounted on a sleeve 229 which, in turn, is rotatably mounted on a reduced portion of adjacent elements 2|8 and 231. The knurled disc 221 is fixed to a member 238 by studs 23| provided at each end of the member. On each of the studs is mounted a planetary gear 232 meshing with the ring gear 2|9, carried by the spider 2|1, and with another sun gear 233 formed integrally with the sleeve 229. Thus the spur gear 228, the knurled disc 221, the planet gears 232 and the ring gear 2|9 constitute a planetary assembly which rotates about the sleeve 229 and comprises the means-by which the numeral bearing shells 222 can be rotated by the actuating mechanism of the machine which drives the gears 228.

For the purpose of carrying tens, means are provided for driving the spider 2|1 and its associated dial shell 222 by means of the spider 2|1 of the next lower order independently of any movement of gear 228.

Secured to the right end of the above mentioned sun gear sleeve 229 is a spider 234 carrying an internal gear 235. A sleeve 231 which also helps to support the sleeve 229 described above, is provided with an arm 238 (see also Figure 3) to which is secured a stub shaft 239 on which a double planet gear 248 and 24| can freely rotate.

The gear section 248 of the double planet gear meshes with the internal gear 235 on spider 234 while the gear section 24| meshes with the sun gear 223 of the adjacent lower order. The part of the sleeve 231 opposite arm 238 is equipped with a gear segment 242 meshing with teeth 243 formed on a lever 244 pivoted to a shaft 245 mounted parallel to the shaft 2I8 and supported by the plates 2|4. This lever 244 is urged clockwise by spring 248 so that a roller 241 carried thereby tends to contact the snail cam 224. In the units order the sleeve 229 is secured directly to the plate 2|4 adjoining it at the right inasmuch as there is no lower order from whichvtens ,Y must be carried.

'I'his arrangement of the several accumulator units permits simultaneous digitation and tens transfer operations known in the art as duplexing In operation, the gear 228 is driven by the actuating, mechanisml and revolves planetary gears 232 about rod 2|6 as a center. Where, as in the units order, the sleeve 229 with its sun gear 233 is stationary, this revolution of gears 232 will, since they are in mesh with -sun gear 233, cause said gears 232 to also rotate about studs 23| and thus drive ring gear 2|9 ahead in the direction in which gear 228 is being driven with a pitch line velocity just twice thatl at which the centers of stub shafts 239 are being revolved. Since ring gear 2|9 is fixed to the indicia bearing s'hell 222, this movement will bring a figure on the shell opposite a sight opening (not shown) of the carriage cover, indicative of the portion of a rotation given gear 228.

Whenever a given amount is thus entered in any one unit of the accumulator, one tenth of that amount will be entered in the next higher unit by means of the carrying mechanism comprising sun gear 223 fixed to spider 2|1 and driving planetary gears 24| and 248, these, in turn, driving internal gear 235 and spider 234 iixed to sleeve 229 of the next higher unit in a direction opposite to that oi spider 2|1, thereby rotating the sun gear 233 integral with the sleeve. If gear 228 and studs 23| are stationary, the movement of sun gear 233 rotates ring gear 2 I9 in the direction opposite to that of gear 233 and therefore in the same direction as that of the lower order dial transmitting the carry. If gear 228 is moving to introduce digitation. as previously described, ring gear 2|9 will move by an amount equal to the resultant of that produced by the rotation of gear 228 and that produced by the rotation of gear 233, the movement of the ring gear, of course, being the resultant of the movement of the sun gear and the displacement of planetary centers. Thus the movement of any higher order dial becomes the resultant of the digitation entry into its own order and the carry movement from the next lower order.

The gear ratios are, oi course, such that the carry movement received by a higher order-dial is one tenth of that of the lower order dial and in order that this movement may be properly transmitted to all units of the accumulator it is desirable that the digitation gear 228 move only in accordance with the values being introduced into the accumulator. To this end means are provided to prevent movement of the gears 228 except as values are being introduced. This means comprises spring pressed pawls 249 (Figure 4) freely mounted on shaft 258, each of which is adapted to engage an associated one of a series of ratchet wheels 2|5A on shaft 245 and fixed to the gear 2|5 in each order. As described above. these gears 2|5 mesh directly with the gears 228 of each accumulator unit and each pawl 243 therefore acts as a brake on one of said gears.

being released on actuation, as will presentlyappear.

Thus, from the foregoing description it is apparent that rotation of a numeral wheel in any order will cause all the numeral wheels in the higher order or to the left thereof, as viewed in Figure 5, to also rotate a certain amount concurrently either in additive or' subtractive direction.

f depending upon the direction of rotation of gears 228, while in all the orders of a lower value or to the right of the last order in which digitation takes piace, no such fractional values are entered.

By virtue of this continuous gearing beween the various orders, the dials 222 are advanced so that the numerals arenot properly lined up at the sight openings in the carriage cover, and in order to overcome this condition, mechanisms have been provided which will turn every numeral wheel to proper alignment with said sight openings directly after an actuation.

The mechanism i'or attaining this line-up operation of said dials comprises the snail cam 224 secured to the left side of each spider 2|1 and which cooperates with and serves to position the spring tensioned lever 244 pivoted at 248 (Figure 3). In this figure the snail cam 224 and lever 244 are shown in a position in which the roller 241 on said lever contacts with the high point of said snail cam, which high point represents the zero position of its associated dial 222. The contour of said snail cams is proportioned in such a manner that each higher digit up to nine on the dials is represented by a successive decrease in size of its radius until the lowest point on said cams represents the digit 9 on said numeral wheels; the values increasing on the dials as well as on the cams in clockwise direction, so that counter-clockwise direction and for subtraction acarrea in clockwise direction when viewing the machine from the right hand side.

When the dipping portion of the carriage 2M is in its lowered position, each lever 244 is normally rocked and held in a xed position in which roller-241 is just clear of snail cam 224. Under these conditions, sleeve 231 and stud 239 (Figure 5) are held in fixed positions, and each dial is in general advanced to a partial position depending on the digitation it has received and the carry from all orders to the right. For instance,-

ldipping portion of the carriage 2N raised, it is desired to back. up each dial by the fractional amount it stands ahead of an `even registration to secure a clear registration in the sight openings. To this end, each lever 244 is allowed to rock clockwise under the tension of spring 2136 as plates 2|4 are raised until roller 241 rests against snail cam 224, which, with the cam shaped as already described, allows lever 24d to rock clockwise by an amount'proportional to the registration on the dial to which the cam is attached. This rocking of each lever 244 rocks each associated sleeve 231 in a counter-clockwise direction carrying stud 239 forward by an amount proportional to the registration on the dial to the right of it, thus rocking ring gear 235 by a corresponding amount and backing up thereby the next dial to the left by an amount each dial is controlled by the snail cam on the next lower order dial so that the proper figure will be squarely lined up to its sight opening in the carriage cover.

Only the dial immediately to the right affects the backing up of a dial and the increment of carry in any one dial is not backed out entirely until that in the one immediately to the right is removed.

As previously mentioned, the dials and cams are rotated counter'clockwise for additive movement and clockwise for subtractive movement while the cam followers 241 follow the snail cams 22d in each order.. Now during subtractive operation it sometimes happens that the value subtracted. is greater than the value from which it is subtracted. In this case the dials will be rotated clockwise, in the direction from 0 to 9 so that if a zero is standing in any order to the left of the last operating order a 9 will appear'. This is because the roller Ztl falls oi the high point on the snail camv 224 to a low point, and in so doing backs up the dial in the next order one digit. If this involves a change from 0 to 9, the change will pass into the next order, Thus a whole series of nines may appear across the carriage to indicate an overdraft. This sequential movement of the dials is termed a "carryover wave.

A counter register for registering the quotient in division and multiplier in multiplication is also mounted in the carriage 200 and is similar in construction to that of the accumulator. Since the details of this counter register and the drive means therefore are disclosed in detail in the above mentioned Avery patent, only a brief description of the function thereof is deemed necessary herein. The several dials (Figure 1) of the counter register are connected to planetary mechanism similar to that illustrated inl Figure 5 and are driven by gears 905 corresponding to those of 228 of the accumulator mechanism. The gears 905 mesh with intermediate gears 903 journaled on rods 904, these latter gearsl each being adjusted to be driven by a gear train including the gear 538 (Figure 14). The particular gear 903 being driven at any one time depends on the position of the carriage and such gear will be driven at a rate of one tooth advance for each main clutch cycle so as to enable the counter dials 90d to register the number of main clutch cycles incurred in each carriage position.

Carriage dipping and release mechanism 'After the heretofore described manually set selection mechanism has been operated and the selection plates H55 correctly positioned by operation of the setting clutch during the early part of its rotation and the locking gate i9l subsequently moved to lock the plates |55 in its adjusted position, entrance of the selected values into the accumulator register carriage is made so that the values will appear on the dials 222 visible through sight openings formed in the carriage cover (not shown). To eiect such entry the intermediate accumulator gears 2l5 (Figure 6) are moved into mesh with the actuating gears it@ by rocking the-several plates 2M and the bail Zita attached thereto downwardly about the piv otal supporting rod M3.

As the platesZ-il are dipped the pawls lil (Figure 4) carried by shaft 250 which, in turn, is earried by the plates 2id, engage a cross rod MSA, carried by the end plates of the carriage, and are caused to rock clockwise against their springs until they are released from the ratchets 2L5A.

To secure dipping or" the carriage at the correct cyclic time means are provided under control oi the setting clutch and are operated thereby to dip the dipping portion of the carriage to enable the selected values to be entered theren into. l

Such means comprises a pair of vertically movable link assemblies, one of which is shown at M0 (Figure 6). Each link assembly includes two links Mil and M2 arranged side by side and having slots and Mt in which extend pins i033 and 15M, the former being secured to the machine framework. A spring lill extends in adjoining elongated apertures formed in the links MII and dit and embraces retaining tenons formed on the links ddl and [M52 at each end of the apertures. This spring normally holds the links lill and. @d2 in their contracted positions illustrated in Figure 6.

Each link (lili has a hook-shaped formation ldd at its upper end which embraces the bail 2 l LEA while each link MZ is pivotally connected at its lower end to a cam :follower arm 449 pivoted at Q50, and carrying a roller @5l which engages a cam Q52 on the setting shaft 35i.

A tension spring indicated by the dotted lines 453 extending between a pin forming a pivotal connection between the link 442 and lever 449, and the stationary pin 443, normally maintains the link assemblies 448 and carriage plates 2|4 in a raised position.

Means are provided for latching the carriage in a lowered position throughout the period of operation of the main clutch regardless of the number of cycles taken thereby, and for returning it to raised position where it is also latched upon termination of clutch operation.

Latches 454 (Figure 6) pivotally mounted at 455 are provided with upper notches 456B and lower notches 456A, either of which may engage lugs 451 formed on the lower links 442 of the link assemblies as at 448. Each of the latches 454 is connected to a rock shaft 463 by a link 459 pivotally connected to an arm 462 xed to the shaft. Spring 458 tensioned between the link 459 and the machine frame tends to maintain the latch member 454 in engagement with the lug 451 and to hold the shaft 463 clockwise. Each notch 456A is offset from the corresponding notch 456B so that when lugs 451 are lowered to a position where they will be engaged by the former the spring 458 will rock shaft 463 further in a clockwise direction than when the lugs 451 are in the position illustrated in Figure 6.

To release the latches 454 in advance of operation of the cams 452 to dip the plates 2|4 about their supporting rods 2|3, means operable by the setting shaft `are provided to rockl the latches 454. This means comprises a pair of complementary cams 386 and 381 (Figure 6A) secured on the setting shaft 35| and engaged by rollers 388 and 389, respectively, mounted on a rocker member 398 which is pivoted at 39| to the machine frame. An ear 398A formed on the member 398 engages an arm 46| pinned to the rockable shaft 463. At the start of a setting clutch cycle the cams 386 and 381 effect rocking of the member 398, arm 46| and latches 454 to release these latches from engagement with the lugs 451. Subsequently, the cams 452 become operative to rock the cam levers 449 and dip the link assemblies 448 and pla's 2|4. Downward movement'of the link assemblies 448 is limited by a resilient stop 461 which is adapted to be engaged by a shoulder 466 formed on each of the upper links 44|.

The devices for releasing the latches 454 to permit the plates 2|4 to be moved from a lowered to a raised position comprise a ratchet wheel 415 (Figure 7) carried directly on the shaft of the driving motor (not shown) and adapted to be engaged by a hooked finger 411I on a bell crank 469 pivotally mounted on an arm 468 also attached to the shaft 463. A spring 418 tensioned between the bell crank 469 and the arm 468 tends to move the nger 411 into engagement with the ratchet 415. It should be noted that the arm 468 and bell crank 469 are shown in Figure 'I in a position they would occupy immediately after having been swung counterclockwise into latch disengaging position by the ratchet wheel 415, following disengagement of the clutch by the clutch dog 413. It should also be noted that engagement of the nger 411 by the ratchet 416 is prevented at the moment just prior to the end of the setting clutch cycle and just prior to the Y engagement of the main clutch by virtue of the overlapping relationship between the camsl 386, 381 (Figure 6A) and 489 (Figure 8). This relationship issuch that the cam 489 starts rocking the main clutch dog 413 sufllciently in advance of the counterclockwise rocking movement imparted to the member 398 by the cam 381 (resulting in clockwise rocking movement of arm 468) so as to cause the hooked flnger 411. to completely miss engagement by the ratchet 415. Furthermore, the cams 452 (Figure 6) and 386, 381 are so arranged that the cam 452 will become effective to rock the assembly 449, 448, and 2|4 downwardly just prior to the complete counterclockwise rocking movement of member 398 and latches 454.

When the carriage is in a lowered position and the main clutch is operating a main clutch control dog 413 is held in a position rocked clockwise about a supporting shaft 414 and out of engagement with the clutch 480. An arm 412 formed integrally with the clutch dog 413 is therefore also held clockwise of the position shown in Figure '1, and an ear 41| formed thereon engages an extension 416 of the bell crank 469 to hold the latter against the action of its spring 418 to prevent the finger 411 from engaging the ratchet 415.

As the clutch dog 413 is rocked counter-clockwise, under the action of tension spring 484, to engage the main clutch 488 and effect disengagement thereof, the similar counter-clockwise movement of the arm 412 will enable the bell crank 469 to be rocked by its spring 418 until the finger 411 is engaged by one of the teeth of the ratchet 415, which will be rotating due to coasting of the motor even though the motor control circuit may be open. The impact of a tooth of ratchet 415 against the finger 411 kicks the bell crank 469 to the left, into the position indicated in Figure 7, thereby rocking the shaft 463 counter-clockwise and effecting release of the latches 454 (Figure 6).

As the plates 2 I4 (Figure 6) move upwardly the lugs 451 on the lower links 442 of the link assemblies 448 engage cam surfaces 456 formed on the latches 454 between the notches 456A and 456B to rock the latches still further in a clockwise direction and thus rock shaft 463 to carry the finger 411 (Figure 7)-of bell crank 469 leftwardly out -of the path of movement of the teeth of ratchet 415. When the carriage reaches its upper position, the lugs 451 (Figure 6) engage in the notches 456B so that the carriage is latched in this position and the finger 411. is maintained out of the path of movement of ratchet 416.

Setting and main clutch operation The present machine employs a setting clutch andfmechanism driven thereby to eiect various operations incident to the commencement of the calculation under the power of the motor.

Operation of the setting clutch 361 (Figure 8) is under the control of the machine operator, particularly through the instrumentality of various operation control keys, such as the division key 188 (Figure 9). The control of the setting clutch is such that upon depression of an add key (not shown), the division key 188 (Figure 9) et cetera, the clutch will be engaged and driven through one cycle (one-half revolution) only, regardless of the length of time that the operating key is held down.

The setting clutch 361, the details of which are disclosed in the above mentioned Avery patent, is controlled by a setting clutch dog 356 rockable Aon a shaft 318 and adapted when rocked counterclockwise, from the position shown in Figure 8, out of engagement with the clutch, to eiect engagement thereof. Normally the clutch dog 366 the ear 312.

with the ear 465 of the main clutch dog 413` to is held in clutch disengaging position by a spring dogand the machine frame.

. The dog 356 is'adapted to be rocked by depression of a bar 316 supported by, a rockable frame 316 and a lever 383 pivoted at 380 and 385, respectively, to a main frame plate 621. 'A bell crank 314 is pivotally connected to the rockable frame 319 by a pin 318 and is notched at its lower end to nt over the ear 312 of the clutch dog356. A spring 311 is tensioned between the bell crank 314 and the bar 316 to normally maintain the notched end of the crank 314 in engagement with' Therefore, when the bar 316 is depressed against the action of a spring 384 tensioned between the lower end of the lever 383 and a shaft 624, the clutch dog 356 is'rocked counterclockwise about its supporting shaft314 to elfect engagement of the setting clutch 361.

As disclosed in the above mentioned Avery patent, means (not shown) operable by a cam driven by the setting shaft 351 are provided to rock the bell crank 314 out of engagement with the ear 312 of the clutch dog 356 during the first setting clutch cycle so that the spring 311 is ef.r fective to cause the dog 356 to interrupt operation of the setting clutch at the end of the first cycle of operation thereof. y

Means operable by the setting shaft 351 are provided to initiate operation of the main clutch 480, the details of which are similar to those of the setting clutch. Secured on the setting shaft 35| is a cam 489 (Figure 8) engaged by a roller 481 mounted on a follower lever 486 which is pivoted on the shaft 310. Lever 486 has an ear 431 extending therefrom and engaging a shoulder 488 formed on an extension of the hereinbefore mentioned main clutch dog 413. Thus, upon rotation of the setting shaft 351 the cam 483 eects rocking of the lever 486 and, consequently, clockwise rocking of the main clutch dog 413 until it is out of engagement with the main clutch 438 whereupon the main clutch is engaged to drive the actuator unit comprising the half and quarter speed shafts 151, respectively (Figure 14) through the presently described division drive and main reverse units (Figures 12 and 13).

In order to maintain the main clutch 4811 in engagement throughout a plurality ci cycles of operation thereof a latch 553 (Figure 8), :xed on a rockable shaft 563, is provided having a notched upper end adapted to engage and latch an ear 4115 on the extension of the clutch dog 413. The latch 562 is pressed against the ear 485 by a spring 554 tensioned between the machine frame and an arm 565 also pinned to the shaft 563. y

An arm 561 also pinned to the shaft 553 is normally engaged by an ear 491 extending from the bar 316. The pivotal supports of the bar 315 are so arranged that upon depression of the bar the ear 491 will be moved to the right, as viewed in Figure 8, enabling the arm 561 to follow under the urge ofthe tension spring 564 so as to permit the latch 552 to drop in under the ear 4135 of the main clutch dog 413.

Thus, as long as the bar 316 is held depressed the latch 562 will latch the dog 413 out of engagement with the main clutch 4311 and the clutch will continue to cycle. However, when the bar 316 is released to allow thesa-me to be raised by its spring 384 (Figure 8), the ear 431 will strike the arm 561 and rock the same counter-clockwise to remove the latch 562 from latching relation l 311 tensioned between an ear 312 of the clutch arrest machine operation.

Control of the motor circuit is effected by the setting and main clutches through a lever 500 (Figure 8) pivoted at 328 and having ears 581 Iand 582 formed thereon and adapted to be engaged by the clutchdogs 413 and 356, rrespectively.

4When either of these dogs is rocked to cause engagement of its respective clutch, it will rock lever 504 clockwise about its pivot 328. Lever 508 is connected to an arm 342, which, in turn, is corinected to a link 331] through a pin and slot connection 343 and 344. The link 338 is connected through a bell crank 331 pivoted at 332 to a second link 333 suspended by an arm 336 pivoted at General calclations drive Power for the various operations of the machine is supplied under control of Vvarious control keys from a motor (not shown) which is connected through a gear train including a gear 534 (Figures 12 'and 14), through themain clutch 466, a division drive mechanism (Figures 12 and 13), and a main reverse mechanism 41 I.

During a division operation the main reverse unit and controls therefor are not affected except to transmit power from a division drive mechanism and the main clutch 480 to the actuator mechanism and, therefore, for the purpose of the present invention, only a brief description of the operation of the' main reverse unit will suffice, the above described Avery patent being referred to for details of this main reverse unit.

The reverse unit 411, division drive unit, and the main clutch 434 are all mounted on a fixed shaft 431 (Figures 12 to 14), the driven side of the main clutch 433 being connected to a rotatable plate 183 to which is secured an internal gear 5111. Gear 5111 meshes with three planet gears 511 mounted on pins 5311 extending from a planet plate 512. This plate is xed on one end of a sleeve 513 rotatable on the shaft 481, while carries three planet gears 515 and these latter gears drive an internal gear 513 secured to a disc 511, which is keyed to a sleeve (not shown) journaled on the shaft 481 and provided with a central plate 531B (Figure 12) secured thereon.

Planet gears 511 and 515 are respectively enmeshed with sun gears 518 and 519. These sun gears are normally held againstv rotation except during subtractive Operations in division, as will appear in the section entitled Division mechanisin and controls, so that the planet gears 511 being rotated by the internal gear 5111 driven by the main clutch 4311 will rotate about their own axes and also revolve about the'shaft 481. Thus, the planet plate 513 is rotated, and since the sleeve 513 connects the plates 512 and 514, the latter plate 514 will also be rotated, and this rotation will be transmitted to the planet gears 515, revolving about the now xed sun gear 519 to the internal gear 516. The disc 511 secured to the internal gear 516 thus transmits continuous rotation to the aforementioned sleeve carrying the plate 588 in the reverse unit 4| I.

Rotatably mounted on the above sleeve on either side of the plate 588 and independent of 584 to which is also secured a gear 538, provided in` a gear train connecting the half and quarter speed shafts |58 and |5I, respectively. This gear train comprises gears 536 to 538, and 548 to 544, inclusive.

As' described in detail in the above Avery patent rocking vof a control lever 42| (Figure 12) which is pivotal on a shaft 422, to one side or the other of a medial position by the reverse con` tro1 mechanism (not shown) will connect the plate 588 with one or the other of the sleeves carrying the gears 536, 548.

Due to the interposition of an idler 531 (Figure 14) intermediate the gears 538and 538 coupling of the gear 586 to the driving plate 588 would cause rotation of the shafts |58 and |5| in a direction opposite to that caused by coupling of the plate 588 to the sleeve carrying gears 536 and 548. However, during addition and all phases of division the plate 588 remains connected with the sleeve carrying gears 536 and 540, rotation of the actuating mechanism in a.

subtractive direction during division being effected by the division drive mechanism as will appear presently.

Division mechanism andcontrols The machine of the present invention includes mechanism for automatically performing division by the successive subtraction method. In accordance with this method a dividend is setup in the accumulator after which the divisor is set shifting the carriage one order to the left and again initiating operation of the machine under control of the division mechanism.

Depression of the division key 188 (Figure 9) initiates motor operation by causing the contacts 331 (Figure 8) to close through engagement of the setting clutch 361. The setting clutch effects release of the locking gate |91 (Figure '1), sensing of the manually set cam unit |46, setting ot the selection plates |55, and relocking of the selection plates by the locking gate |91. Also, during operation of the setting clutch. mechanism is set permitting each o! the previously described levers 244, carrying rollers 241, to follow the contours of their associated cams 224 (F18- ures 3 and 9). The setting clutch also causes engagement of the main clutch 488 which, in turn, effects a negative driving through the division drive (Figures 12 and 13) of the quarter and half speed shafts |58 and |5| .(Figure 14) at a much higher speed than is employed during Vother operations of the machine and intermittently instead of continuously. The division key is latched in depressed position and enables the main clutch to continue to cycle so as to subtract the value in the keyboard from that in the accumulator any number of times until the value in the operated orders is reduced to zero and an overdraft occurs.

Control of setting clutch during division The division key 188 (Figure 9) is mounted on one side of a supporting plate 62| and the key stem 18| thereof is guided on pins 182, being biased in an upward direction by a spring 183 extending between the upper pin 182 and an ear lformed on the key stem 18|. The key stem 18| also includes a projection 184 which extends through an opening in the supporting plate to retain two operation control levers 185 and 186 (see also Figures 18` and 19) in neutral positions when the division key 188 is raised.

The levers 185 and 186 are supported on a shaft 181, the lever 185 being secured to the shaft and the lever 106 being freely pivotable thereon. The lever 185 is provided with an enlarged head at the upper end thereof forming a latching surface 1|8 and carrying a roller 1|| which overlies the operating bar 316 (Figures 8 and 9) so that clockwise rocking of lever 185 causes depression of the bar 316 to` engage the setting clutch and start the motor as described hereinbefore. A spring 1|2 tensioned between the lower ends of the levers 185 and 186 normally maintains an ear 1|1 on the lever 186 in engagement with the upper end of the lever 185.

The lever 185 has a lug 1|4 formed on the 11p- -per end thereof which is capable of being enare both biased in a clockwise direction by springs 1|8 and 1|6,'the rearward tip of latch 189 maintained in contact with the .projection y184 on the ,division key stem, while the latch 188 is normally maintained in contact with the ear 1|4 on the upper end of the lever 185. The rearmost end of this latch 188 may/be engaged by a lug 128 on an arm 12| which is pinned to a rocking shaft 638 forming part of a pulsating mechanism to be described later so as to remove the shoulder 1 |5 from latching engagement with the ear 1 1 of lever 186.

Lever 186 is U-shaped, as shown in Figure 18, and includes an arm 122 which is pivotally connected to a link 123 which is, in turn, pivotally connected to a downwardly extending arm 124 of a division drive control lever 125 (Figures 9, 12, 15, and 16) mounted on the shaft 422 and held thereon by a screw 121. The lever 125 is biased in a counter-clockwise direction by a heavy spring 126 tensioned between the arm 124 andthe machine frame. The bias of this spring urges lever 125 counter-clockwise and levers 185 and 186 clockwise. However, the levers 185 and 186 are normally restrained against such movement by the projection 184 of the division key stem 18|.

Thus, upon depression of the division key 188 and release of the lever 185 by the projection 184, the spring 126 is free to rock levers 125, 185, and 186, causing the roller 1|| on the lever 185 to depress the setting clutch controlling Ibar 316 to initiate operation of the setting clutch.

low the contours. of their associated snail cams Conditioning of the division drive Rocking 'movement of the lever 125 (Figures 9, 12, 15, and 16) by the spring 125 is utilized to condition the division drive to intermittently roin the position illustrated in Figures 9 and 15,

to engage a complementary notch in a box cam 12B (Figures 9 and 12) to restrain Said cam against rotation.- Another arm 129 is provided on the lever 125 and normally extends outside of the path of rotation od three pins 130 carried on the planet gear plate 512 described hereinbefore in the section headed General calculations drive, these pins 130 supporting the planetary gears 51| (Figure 12) When the lever 125 is rocked in a counterclockwise direction, aswviewed in Figure 9, the arm 125A is disengaged from the cam 128 while arm 129 is positioned under one of the pins 139 so as to restrain the planet plate 512 against rotation. Since. the planet plates 512 and 514, which are connected by sleeve 513, are held from rotation by the engagement of arm 129 of lever 125 with one of the pins 130 (Figure 9) and the box cam 128, to which the sun gear 518 is secured, is released, planet gears 51! .will now :be rotated about iixed axes and-transmit rotation to the sun gear 518 at a relatively high speed. The cam 128 having the contour illustrated in Figure 9 and now driven by the sun gear 518 will successively engage each of iive pins 131 riveted to a gear 132 (Figures 9, 12 and 13) journaled on the shaft 422 so as to intermittently drive this gear 132.

Gear 132 drives gear 133 which is secured to a larger gear 134 meshing with a pinion 135 (Figure 13) keyed to the sun gear 519. Gear 519, as previously mentioned, meshes 4With planetary gears 515 which mesh within the internal gear 516 rigidly secured to the disc 511 of the reverse unit 4H.

In division, with the planet plates 512 and 519 (connected by sleeve 513) held stationary, when lever 125 is rocked in a counterclockwise direction, as viewed in Figure 9, the drive from the internal gear 519 to' the internal gear 516 is through the ,planet gears 51|, to the box cam 129 which is xed to the sun gear 518 and driven by planet gears 511. The box cam intermittently drives gear 132 and gear train 133, 139,and 135, planet gears 515, and through these, drives. the internal gear 516 andrdisc 511 secured thereto and iinally drives a part of the reverse unit il l.

Because of the sizes and arrangement of the various gears in the division drive train just 'dee4 direction.

Setting' of snail cam followers during division During division the rollers 291 on the levers itt (i'igures i, 3, 5, and 9)are permitted to iol- 224 when the carriage is held dipped during subtractive operation. In the order to the left of the last operated order an overdraft is sensed and is transmitted to division sensing mechanism which operates to stop the machine and initiate a single cycle of additive actuation called the corrective or restoration cycle. Itis only necessary that the first lever 244 to the left`of 'the last operated order being sensed be operative to control the sensing mechanism, but all levers 241 are permitted to follow the contours of their associated snail cams 224 so that a carry 'Wave'- can be transmitted acioss the accumulator register as described hereinbefore in the section headed "Accumulator mechanism so that an' overdraft occurring in any order of the accumulator register may be transmitted to the conthe shafts 259 and 245, being supported by the dipping plates 214 are moved down with respect to the shaft 146A which is carried by the several carriage brace plates 208 (Figure 3).

Upon depression of the division key 100 (Figure 9) the spring 126 pulls lever 125 counterclockwise as disclosed hereinabove and this movement enables the bell crank 146 secured to the rockable shaft 146A to be moved by the levers 294 under action of their springs 246 to the position illustrated partly by the dotted lines in Figure 9, thereby allowing the rollers 241 on each lever 244 to engage and follow its snail cam as long as the carriage is held dipped during a subtractive actuation.

The bell cranks 146 are normally held in the position shown in Figure 9 by a lever 145 pivoted on a shaft 191 supported b y the machine frame and extending into contact at the lower end thereof with a roller '1&9 mounted on a rock plate '199 which is pivoted on a stud 150 extending from the machine trame.' The rock plate 149 is pivotally connected to one arm of a bell crank 15l, pivotally mounted at 152A to an arm 152 fixed to a rockable shaft 19H. A pin 154 mounted on the other -arm. ci the bell crank 151 extends through a slot 159A in an arm 153 of the lever Upon rocking of the lever 125 by the tension spring 129 as described hereinbefore, the arm 153 raises the pin 154 and, due to the particular arrangement of the bell crank 151, lever 152 and rock plate 199, causes simultaneous counterclockwise movement of lever 152 and plate "M9 Thus, the plate 199 is rocked until its roller 199 reaches the position illustrated in dotted lines in Figure 9 and the lever 145 is therefore tree to be rocked by the bell crank 199. .Rocking movement or" lever 152 also rocks shaft 19t to condition the overdraft sensing mechanism to be described presently.

iiperation of sensing mechanism in carryover operation During a division operation and whileactuation taires place in a subtractive direction, the snail cams 929 (Figures 3, 9 and 29) in the operated orders are rotated clockwise and when an over carry operation takes place the lever 2294iof the sensed order moves from the highest to the lowest point of its cani, this moving taking place when the diai moves from zero to nine registration. The drive is thereupon conditioned, as before mentioned, for one cycle of positive operation, bell crank 146 being returned to its original position illustrated in Figure 9 to hold the levers 244 with their rollers 241 clear of the high points of the snail cams 224. The latter can therefore rotate freely in an additive or counterl clockwise direction for one cycle.`

The overdraft or carryover sensing mechanism comprises levers 156 and 151 (Figures 9, 10 and the former lever having a projection 166 extending adjacent the foot 164 on the lever 244 in the order to the left of the last directly operated order. Lever 151 is pivotally mounted on a shaft 156 and is connected by a link 616 to an arm 166 ilxed to the shaft 16|. A lever 166 in the form of an inverted U-shape is pivoted to the lever 151 at 165 and has an ear 166 thereon which overlies an extension of the lever 151 to limit counter-clockwise rocking of the lever 156 relative to lever 151. A spring 166 tensioned between an arm 161 of lever 156 and the lever 151 normally urges the lever 156 counter-clockwise to the limit of its movement as restricted by the ear 166.

When the division key 166 is depressed and the lever 125 is rocked by spring 126 as before described the shaft 16| is rocked counter-clockwise and this movement is transmitted by the link 156 to the lever 151 so as to swing a projection 166 on the lever 156 into engagement with the foot 164 on the particular lever 244 which is positioned over the projection 166. This is' the first lever 244 to the left of the last operating order. It should be notedthat during this period the accumulator supporting plates 2|4 will be held dipped in thev position illustrated in Figure 20 in a manner described hereinbefore. Thus, in division the lever 151 will always be rocked counter-clockwise to its full line position illustrated in Fig. 20, while the lever 156 which may during this period be considered as part of the cam follower means will be urged by the spring 166 to follow the foot 164 of the associated roll carrier lever 244. Therefore, with the foot 164 in that position corresponding to a zero registration on the corresponding dial 222 as illustrated in full lines in Fig. 20, the lever 166 will describe a maximum clockwise movement with respect to lever 151.

The moment an overdraft occurs, the roller 241 on the lever 244 of the overdrafted order drops from the highest point on the associated snail cam 224 to the lowest point thereon, in which case the foot 164 moves to its position 164A and permits a counter-clockwise movement of the sensing lever 156 which is employed to stop the division drive and initiate a single Acycle of additive rotation during the correction cycle. The mechanism for securing this operation will now be described.

The mechanism operated as a result. of the sensing of an overdraft includes arms 116 and 11| (Figures 9, 15, and 16) which are secured to a rockable shaft 112. A spring 116 tensioned between the machine frame and the arm 11| normallymaintains the arms 116 and 11| in a clockwise position, as illustrated in Figures 9, 15, and 16, this movement'being limited by a pin 114 extending from the machine frame.

A yieldable tip 116 is pivoted on the lever 116 at 116a and has a shelf 116 formed thereon and adapted to be engaged by the arm 161 of the lever 166. A tension spring 111 extending between tip 116 and the lever 116, normally 1I maintains the tip rocked to the extreme clockwise position, illustrated in Figure 9, with a lug formed on the tip in engagement with the lever 110. Thus, the tip 115 may yield when rocked counter-clockwise about the lever 110. The purpose of this yieldable connection is to make it possible for the sensing mechanism to distinguish between an overdraft and a normal nine registration without overdraft, as will appear presently.

The arm 11| (Figures 15 and 16) is formed with a hook 116 at the upper end thereof which is adapted to engage an ear 119 of a three armed dog 166 pivoted on the pin 154 so as to cause the dog to rock clockwise when the pin 154 is raised by counter-clockwise rocking of the lever at the start of the division operation as was described hereinbefore.

The dog 166 has an ear 16| thereon which, upon sensing of an overdraft, is adapted to engage one of a pair of diametrically opposed projections 162 on the aforementioned plate 166 (Figures 12, 15, and 16) secured to the internal drive gear 516 of the division drive unit. The dog 166 also includes an arm 164 which is pivotally connected to the upper end of a double acting compression-expansion link assembly 166 extending between the dog 166 and the lever 126. This link assembly functions in somewhat the same manner as the link assembly 440 (Figure 6) and comprises a -link 166A (Figure 17) pivoted at its upper end to the arm 164 of dog 166 by a stud 164A. This link 166A is provided with an elongated slot at the lower end thereof which embraces a stud 161 lsecured to the lever 126. A second link 166B is pivoted on the stud 161 and has an elongated slot embracing the stud 164A, both links having adjoining apertures therein in which extend a compression spring 166C fitted over tenons provided on each link and extending into the apertures at each end thereof. This link assembly, because of the arrangement ofthe spring 166C, tends to maintain a normal length, as illustrated in Figure 15,- regardless of whether the link assembly is shortened or lengthened beyond such normal length.

At the beginning of a division operation the lever 125 isas before stated, rocked counterclockwise, raising the pin 164, arm 162, bell crank 16|, and rock plate 146 into the positions shown in Figure 16, as well as moving the stud 161 to a new position which results in the dog 166 being rocked counter-clockwise until its ear 116 engages the hook 116 forming a latch therefor. Due to the fact that the pin 154 is raised a greater distance than the stud 161 of the lever 126, the linkassembly 166will be extended, compressing the spring 166 thereon, so that the same will become active to rock the dog into engagement with the plate 166 whenever the lever 11| is rocked counter-clockwise to unlatch the ear 116 on the dog 166.

When an overdraft occurs during division, the lever 166 is rocked forward from its full line position illustrated in Figure 20 towards its alternate position illustrated by the dot and dash lines 166B at which time the arm 161 engages the yieldable shelf 1162 and causes rocking of the arms 116 and 11| to unlatch the dog 166, even though a yielding connection is provided between the member 116 and the arm 116, as will appear presently. The yielding connection is provided to avoid a trip-oi! in case the control order has a high digit, for example a "nine," when the division is first started in that order but to secure a trip olf when the nine comes into such order following the registration in that order having been reduced to zero and therebeyond. o A

` To secure this result the arm 161 on lever 156 is arranged so that it will be at such a radius from th'axis of the pivot shaft 156 when the lever 156 is rocked to its extreme counter-clockwise position relative to the lever 151, as illustrated in Figure 9, that as the lever 151 is rocked forward at the start of a division operation,` the arm 161 will passfreely beneath the shelf 116..

under surface'pf the shelf 116, rocking it in a counter-clockwise direction about its pivotal con. ynection 115a relative to the arm 110. By the ytime the registration on the dial. 222 has been reduced to zero the arm 161 will have rocked completely to the rear of the shelf 116 as indicated by the full 4lines of Fig. 20 and allowed the yieldable tip 115 to fall back into its normal position illustrated in Figure 9. When thereafter theroller 241 on the lever 244 drops off the high point of the snail cam 224 tol the lowermost point thereof and allows the lever 156, to be rocked in a counter-clockwise`directiori to its position 156B (Fig. 20) by its'spring 166, arm 161 thereonis brought down on the shelf 116 rocking the tip 115 and arm 110 together as an integral unit in a counter-clockwise direction. Due to the downward component of this latter movement of lever 156, arm 161 will not be capable of rocking the yieldable tip l115 aboutv its .pivotal connection 115a, but the lug to which the spring 111 is attached will engage and force the lever 110 counter-clockwise. Therefore, arm 11i (Figures i5 and 16) will also be rocked counter-clockwise releasing the clutch dog 180. Upon release ci vdog 180 thel Spring' 185C in the link umt 18S rocked ina clockwise direction, the link supporting p in1154 being so arranged that the path ci movement thereof is substantially concentric about the Shaft 48|. .The pin 154 thus rocks the lever.125 clockwise retensioning the spring '1i-ci and-forcingarm 125A torreengage the cam '18 (Figures 9 'and l2).1 Therefore since the 129 is also released from engagement with one of the pins 130 on'- the planet plate at time,l the intermittent reverse movement is rested and themachine brought to a standstii As the lever 125is being rocked in a clockwise direction, the linkv123 (Figure 9) rocks iev-e: 1% toy the leftuntil its ear 111 is latcherl by shoulder 1i6jormed on the latch' its. Lever we is, however, notl returned at this time, since is retained by the rightmost shoulder, asgiewed in Figure 9, of the nose 115 of the latch 1513, thereby maintaining the bar 316 depressed www .effect a subsequent additive restoration cycle of the main clutch.

During all main clutch cycles including restoration cycle a pulsating cani 63| (Figure 2) attached to the driven side of the main clutch shaft 638 (see also Figures 9 and 1K1) to which 1 is also pinned, as before stated, the arm 12| having an ear 120 thereon underlying the latch 106. Thus, during the restoration cycle, the arm' 12| rocks the latch 108 upward to -release the lever 105 and the spring 1|2 becomes active Vto rock this lever counterclockwise until it assumes its normal non-operating position, illustrated in Figure 9, and releases the division key 100. Al-

though the arm 121 is rocked upward during each main clutch cycle to rock the latch 106, it will not become eectve during negative operation in division since the lever 106 is held in a rearmost position at this time and, therefore, even though the lever 10E is momentarily released from the latch 106 it is held in position by lever 106.

As the spring 126 is retensioned at the end of'v the negative actuation in division by movement of the lever 125, the clockwise movement of pin 154 tends to cam the dog 180 (Figures 15 and 16) from engagement with the projection 162 on the rotatable plate 133. This camming of the dog ii is completed after the member 166 has been iatched in a forward position by the latch 109 so that the spring 126 is latched under tension while the plate `183 is permitted to proceed with the restoration cycle. As the divisionrkey is subsequently released and the projection 104 thereof moved along the face 1|0 of the member m5, the projection 101i strikes the free end of the latch 169 rocking it slightly counter-clockwise y additionai quotient by repeating the operations described.

l claim:

i. in a caicciating machine having an accumulator comprismg a series oi'lregistering ele- Y ments; an overdraft sensing mechanism comprisa connected to one of saidfele.

. scents and ha a gradually increasing/radius nine tenths of its circumfer .i cheaply decreasing radius within the pci-'tion of circumference, cam telf wer responsive' to the i'eg=l istration of an overdraft by said accumulator including a member actuated by said cam follower means upon inward movement of a portion thereof along the aforesaid sharply decreasing radius of said cam.

3. In a calculating machine having an accumulator comprising a series of registering elements; an overdraft sensing mechanism comprising a radial cam connected to one of said elements and having a gradually increasing radius for substantially nine tenths of its circumference and a sharply decreasing radius within the remaining portion ofits circumference, cam fol.. lower means, and means responsive to the registration of an overdraft by said accumulator including a twopart device one part only of which is operable by said cam follower means upon out- 4ward movement of a portion thereof along the aforesaid gradually increasing radius of said cam, but both' parts of which are operable by said cam follower means upon inward movement of said portion thereof along the aforesaid sharply decreasing radius fof said cam.

4. In a calculating `machine having an accumulator comprising a series of reversibly operable registering elements and actuating mechanism therefor; the combination with an overdraft sensing mechanism comprising a radial cam connected to one of said elements and having a gradually increasing radius for substantially nine tenths of its circumference andv a sharply decreasing radius' within the remaining portionv of its circumference; of cam follower means spring activated to follow said cam, control means, settable to control the direction of operation of said registering elements by vsaid actuating mechanism, and means actuated by said control means for withdrawing said cam follower means from cooperative relationship with said cam wh'en said control means is set to cause operation of said registering elements in one direction.

5. In a calculating machine, accumulator mechanism, rotary actuating mechanism therefor, driving means for said actuating mechanism comprising alternatively operable intermittent .drive and continuous drive transmission mechanism, means for initiating operation of said actuating mechanism by vsaid intermittent drive on mechanism, and means responsive to an overdraft registration in said accumulator mechanism for disabling said intermittent drive tron and enabling said continuous drive on mechanism.

6. In ay calculating machine having an accumulator mechanism and actuator mechanism therefor; the combination -ol-.drive means for said actuator mechanism comprising selectivelyl continuous drive transmission and enabling said intermittent drive transmission.

8. In a calculating machine having an accumulator mechanism, actuator mechanism therefor, and division control mechanism including a division initiating member; the combination of drive means for said actuator mechanism comprising selectively operable intermittent drive and continuous drive transmissions; switching means for disabling said continuous drive transmission and enabling said intermittent drive transmission, latching means for holding said switching means from operation, and means responsive to operation of said initiating member for releasingv said switching means from'said latching means and means responsive to an overdraft of said accumulator mechanism for again holding said switching means from operation.

9. In a calculating machine having au accumulator mechanism, actuator mechanism therefor, and division control mechanism including a division initiating member; the combination of drive means for said actuator mechanism comprising selectively operable intermittent drive and continuous drive transmissions; means normally maintaining said continuous drive transmission enabled, means responsive to operation of said initiating member for disabling said continuous drive transmission and enabling said intermittent drive transmission, sensing mechanism operable in response to an overdraft of said accumulator mechanism for disabling said intermittent drive transmission and enabling said continuous drive transmission, means normally maintaining said sensing mechanism ineiective to sense an overdraft, and means responsive to operation of said initiating member for rendering said sensing mechanism effective.

10. In a calculating machine having an accumulator' mechanism, actuator mechanism therefor, and cyclically operable drive means; the combination of an intermittent drive transmission for transmitting power from said drive means to said actuator mechanism, said intermittent transmission being adapted to arrest operation of said actuator mechanism during a predetermined period in each cycle of operation of the drive means, and means operative during the said period of a, cycle of .operation 'during which an overdraft registration is effected in said accumulator mechanism for disabling said transmission.

11. In a calculating machine having an accumulator mechanism, actuator mechanism therefor, and cyclically operable drive means; the combination of selectively operable intermittent drive and continuous drive transmissions operable in opposite directions for transmitting power from s aid drive means to said actuator mechanism, said intermittent transmission being adapted to arrest operation of said actuator mechanism during a predetermined period in each cycle of operation of said drive means, division control means including means for initiating operation of said actuator mechanism by said intermittent tm o and means operative during the said period of a cycle of operation during which an overdraft registration is effected in said accumulator mechanism and responsive to said overdraft for disabling said intermittent transmission and enabling said continuous HAROLD T. AVERY. 

